Delivery mechanisms ensuring the transfer of punched sheets from a press to a waste ejecting device



Aug. 17, 1965 3,201,115

J. KURY DELIVERY MECHANISMS ENSURING THE TRANSFER OF PUNCHED SHEETS M A PRE SS TO A WASTE EJECTING DEVICE 5 Sheets-Sheet 1 FRO Filed July 25, 1963 INVENTOR JOSE F KURY Aug. 17, 1965 J. KURY 3,201,115

DELIVERY MECHANISMS ENSURING THE TRANSFER OF PUNCHED SHEETS FROM A PRESS TO A WASTE EJECTING DEVICE Filed July 25, 1963 5 Sheets-Sheet 2 EMAX.

INVENTOR JOSEF KURY I J. E E

Aug. 17, 1965 J. KURY DELIVERY MECHANISMS ENSURING THE TRANSFER OF PUNCHED SHEETS FROM A PRESS TO A WASTE EJECTING DEVICE 5 Sheets-Sheet 3 Filed July 25, 1963 INVENTOR JOSEF KURV 3,201,115 I) SHEETS J. KURY Aug. 17, 1965 DELIVERY MECHANISMS ENSURING THE TRANSFER OF PUNCHE FROM A PRESS TO A WASTE EJECTING DEVICE Filed July 25. 1963 5 Sheets-Sheet 4 INVENTOR JOSEF KUR) Aug. 17, 1965 J. KURY 3,201,115

DELIVERY MECHANISMS ENSURING THE TRANSFER OF PUNCHED SHEETS FROM A PRESS TO A WASTE EJECTING DEVICE Filed July 25, 1963 5 Sheets-Sheet 5 INVENTOR JOSE F KU/ZV DELIVERY MECHANISMS ENSURING THE TRAN S- FER OF PUNCHED SHEETS FROM A PRESS TO A WASTE EJECTING DEVICE Josef Kury, Pully, Switzerland, assignor to J. Bobst and Son S.A., Prilly, near Lausanne, Switzerland, a corporation of Switzerland Filed July 25, 1963, Ser. No. 297,578 Claims priority, application Switzerland, Mar. 22, 1963,

H 3,684/ 63 6 Claims. (Cl. 271-51) This invention relates to apparatus associated with press punching operations on a sheet material, such as paper or cardboard, in which the press is combined with a waste ejecting device.

The press punching requires an intermittent transport of the sheets which must be immobilized when punched,

whereas wastage is removed in continual motion, for instancegby meansof cylindricalmernbers, the periphery of which is provided withneedles or spurs for picking and removing the wastage.

This difference between the conveying method of processed sheets and that of sheets submitted to the ejection introduces some problems, in particular due to the fact that it is necessary as far as possible to avoid subjecting the punched sheets to sudden acceleration and slowing down which is likely to tear them.

In the particular case in which the sheets are driven through the press by gripping bars led between two endless chains alternatively moved and immobilized, there are still other problems to be dealt with, as it will appear further in considering the following drawings wherein:

FIGURE 1 is a diagrammatic illustration of a press with an ejecting device;

FIGURES 2-4 are diagrammatic illustrations of portionsof the apparatus of FIG. 1 on enlarged scale showing various stages of operation of the apparatus;

FIGURES 5 and 6 are diagrams of the kinematics of the apparatus of FIG. 1; and i FIGURES 7-13 show the detailed construction of the apparatus diagrammatically illustrated in FIG. 1.

In FIG. 1 the press is on the right and the ejecting de- Vice on the left-hand side of the drawing.

The press is shown in part in section, wherein there is provided upper fixed platen 1 and a movable lower platen 2, driven up and down periodically.

In the front and back of these platens run two endless chains which are symbolically. represented by the dash and dotted line 3 passing over chain wheels not represented. 1

Between these chains are. arranged gripping bars, one of which is at 4, driving a sheet of paper or cardboard 5.

In operation, such a bar stops just after the platens, on the outside of the latter (therefore ontheir left side on the drawing) and secures asheet between them. The platens are closed under pressure, the punching is carried out,

thenthe wheel chains resume their motion, while the platens are separated from each other, as illustrated, the punched sheet is drawn from between the platens and occupies practically the posiition shown in FIG. 1 at the moment it reaches its greatest conveying speed which is at the same time as that of the feeding between the plat ens of an unprocessed sheet driven by the next bar.

On the left of the elements already mentioned are rollers6, 7 feeding the sheets into the ejecting device. The rollers 6, 7 lead the sheets, such as 5, above the drum or discs 8, the'periphery of which is provided with needles or s purs 9, picking the, waste on its passageopposite to a grooved roller or above discs 10. This passage takes place at constant speed.

The presence and passage of the gripping bars introduces the following problemsi i To insure their passage, it is first necessary that at least United States Patent 0 one of the rotating organs receives the sheets at the mo rnentary conveying speed of the latter, for instance, the

organ 11 facing the rotating organ 12 has a notch 13 on a part of its circumference.

Additionally, it is necessary that these organs 11 and 12 seize the sheet at its conveying level which at. the level of the upper face of the bar and at its conveying speed.

sheet is to be lowered and put on that or those supports on which it has to slide and at the level at which it will be received by a second pair of organs 15, 16, pushing it finally between the feeding rollers 6 and 7 ofthe ejecting device. j

Whereas in known devices the lower organ or organs 11 were in the trajectory of the bars, the lowering of the conveying level requires that the upper organ or organs 16 will have to allow the bars to pass, hencethe notch 18l When there are one or several conveying organs or supports, this means that a series of coaxial discs will generally be preferred to cylinders and that the suppor'tswill' then be made up of bars passing between those discs. The present invention aims at resolving simply the various problems established by-the working conditions already stated in the case of a press with conveyance of the process sheets by gripping barssecured between two endless chainsput alternatively in motion and immobilized.

The mechanism according to the invention comprises to this end, rotary conveying organs arranged near the locationwhere each gripping bar removes a processed sheet from between the platens, reaches practically its highest speed, said organs being profiled so as to seize the sheet immediately. after release from the bars, the motions of these elements being at that moment synchronized in such a way that the conveying speeds ofthe bar and rotary conveying organs are equal, but controlled so that the rotary organs are then immediately subjected to a slowf ing down, making it possible for the bar to move olf from the sheet lowered then by the rotary conveying organs to a level beneath the conveying plane of the bars, the sheet being fed at said lowered level toother rotary conveying" organs driven at constant speed ,andleading the sheet through a waste ejecting device, while the first rotary conveying organs are brought back to the original level to receive the next sheet. 3

In FIG. 2 there is shown diagrammatically the chains 3 (there beingtwo spaced chains at opposite edges of the sheet) passing over chain wheels not represented, turning in the direction of the arrow, to tran sport the gripping bar 4 when it moves at its highest conveying speed. I

In the diagram of FIG: 5-, the curve A. represents,

when read from right to left with thetime as abscissae and the traveled paths as ordinates, the displacement of bar 4 during a working cycle. The immobility at A corresponds to the working of the press, at which time the bar is motionless, then there is acceleration at 4A", changing into the maximum speed already referrred to, slowing down and new immobilization, and so on.

The correspondingcurve of thespeeds B shows that when considering the ordinates; as measuring the speed.

.There is immobility at B and maximum speed at B Reverting to FIG. 2, B occurs at the moment when the conveyed sheet Sis seized by the rotary conveying i organs 11 and 12, the circular notch 13of the organ 11 previously ,allowingthe bar 4 to pass.

Just when the sheet is seized, theperipheral speed of 'speed of the bar at the moment of its speed B 3 these organs is equal to the conveying speed of the bar.

The curve C of FIG. 5 shows the variations of this speed in comparison with the speed B of the bar and to the same scale.

Normally driven at a mean conveying speed C, the conveying organs undergo an acceleration, to reach the It is then that the organs 11 and 12 seize the sheet 5.

In order to separate the sheet from the bar, ie to remove the sheet from the grips after the point B the peripheral speed of the conveying organs diminishes at a greater rate compared to that of the conveying bar (compare the cruves C and B) and reaches a minimum (C This is the position of FIG. 3, in which the front edge of the sheet occupying the position reaches the rotary conveying organs 15,16 turning at constant speed in which their peripheral speed, represented by the line D of FIG. 5 is precisely equal to C,,,,,,. This is the feeding speed of the sheet into the ejecting device by the rollers 6, 7 or other equivalent rotary conveying organs.

But at thesame time the sheet 5, after having been slowed down so as to be separated from the bar 4, is driven at the final constant speed C it has been shifted, lowered above the conveying plane by the bars, the organs 11, 12 having been to this effect lowered to the positions 11', 12' of the FIG. 3

This vertical displacement is represented by the curve B of the FIG. 6, the abscissae of which correspond to the times of the abscissae of the FIG. 5 and the ordinates to the aforementioned vertical displacements. It appears that after E corresponding to B there is lowering, first down to E, corresponding to the position of the FIG. 3, that is with sheet practically on the guides or supports 14. e

The notched organ 11 having rotated by half a turn to 11', corresponding to the arc embraced by its notch 13, it ceases at that moment to exert an action on the said sheet, which will be in a position to be driven at its final constant conveying speed.

During this time and lowering of its speed, the gripping bar will have reached 4'.

By the time it takes to reach its position of immobilization 4" of the FIG. 4, the organ 11 will have again performed a half turn, whereby it would have to press again the sheet against the organ 12, but at a peripheral speed unsuitable for the conveying speed of the sheet 5"; For this reason it is necessary to separate momentarily these two organs (positions 11" and 12" of the FIG. 4) by lowering momentarily 11 according to the portion E" of the curve E of the FIG. 6.

In order to secure a diameter of reasonable size for the organ 11, allowing it at the same time to reach the peripheral speed B it will be preferable to make it perform three turns for each press working cycle.

Between the sheet seizing position of that of FIG. 2 and that of the slowed down conveyance with lowering in FIG. 3, half a turn has been performed. Another half turn has been performed between the latter position and that releasing the sheet in FIG. 4. From thisposition, back to the position of FIG. 2, there would then be two turns performed at the mean speed C, ending by the acceleration up to'B at the same time there will be elevation and return to the grippinglevel of the sheet 5.

These various motions can be easily carried out by the embodiment described hereafter by way of example.

FIG. 7 corresponds practically to a vertical cross-section drawn through the shafts of the organs 11 and 12.

FIG. 8 shows, in relation to FIG. 7, elements extending in the front of the plan of this figure, under the level of the'lower 'arbor crossing it from left to right, which the FIG. 8 represents partly broken away.

On the right and left of FIG. 7 are profiled swinging plates supporting the shafts and main turning organs and imparting to them the required motion.

FIGS. 9, 11 and.

4.- 13 show the right-hand parts, seen from within toward the exterior of the device and in three important positions. FIGS. 10, 12 and 14 show the left-hand parts in the same three positions, and seen likewise from within the device.

Reverting to FIGS. 7 and 8 the following details are shown:

The lower arbor 17 sets off a series of conveying rotatory organs 18, which are the equivalent of the notched organs 11 of FIGS. 1-4, which will henceforward be called segments. The segments are surmounted by the pressing organs 19 (corresponding to organs 12). While the pressing organs 19 are integral with their common arbor 20, the lower organs 18 are rotatively free from the arbor 17, and revolve with a socket 21 joining them together, said socket 21 having ends which are terminated by cog-wheels 22 and 23. The wheel 22 provides a connection between the socket 21 and the arbor 20 through gears 24 and 25 and an interposed cog-wheel 29 which appears in FIGS. 9, 11 and 13.

This arrangement corresponds to the conveying elements 11 and 12, FIG. 7 showing a conveying bar 26 between two chains 27 and supports 28, the latter corresponding to 14 in FIG. 2.

The bar 26 and the chains 27 are moved from the back to the front in the drawing plan of FIG. 7.

The bar 26 is shown in front of the segments 18 to which it gives up the sheet it conveys (FIG. 2).

FIG. 9 is a side elevation of the right-hand part of the FIG. 7 which shows in particular the arbors 17 and 20 and the socket 21 (in section), the gears 22, 24, 25, and also the intermediate cog-wheel 29 referred to above. The relations between these various cog-wheels are such, that the conveying rotary organs 18 and 19 which they link turn at the same peripheral speed. That is a condition for the correct driving of the processed sheets 5, taken over from the gripping bars 26.

The arbor 17 and the shaft 30 of the cog-wheel 29 turn in a plate 31 with a profiled end which is oscillatory around a fixed shaft 32 (see also FIG. 8) while the shaft 33 of the cog-wheel 24 and the arbor 20 are secured by a rocker or yoke 34, terminated by a nose 35, turning around the shaft 30 on .the plate 31 by the action of a spring 36, acting upon the rod 37. The swinging of the yoke 34 is limited by the adjustable stop-screw 38 which contacts,

the plate 31.

On the arbor 17, and behind the said plate 31 in relation to the position of the FIG. 9 is a cam 39.

This cam serves to raise and lower the elements already described, taking rest on.a small roller 40 of immovable position. FIGS. 7 and 9 correspond to the highest position (E of the curve of FIG. 6).

The only two fixed elements described up to now, namely the shaft 32 and the small roller 40, are supported by a frame side'wall which appears in section at 41, in FIG. 7, but which has been broken away in FIG. 9 where it occupies the background.

The fixed wall 41 is fitted with an adjustable stop 42, the block 42' of which is integral with the said wall, and consequently is likewise fixed. This stop is designed to cooperate with the nose of the yoke 34.

As shown in FIG. 7, there is on the opposite of.th wall 41 of the frame a second fixed wall 43 which is parallel to wall 41 (see also FIG. 8) and which supports a second small roller 44, identical with the small roller and set on the same geometrical axis. The roller 44 cooperates with a cam 45 which is identical to the cam 39, set on the other end of the arbor 17 and is of same adjustment or keying. Accordingly, when arbor 17 and the said cams turn, there is displacement of its two ends according to an identical arrangement for both. This rotation is brought about by the cog-wheel 46, which will be referred to later on.

FIG. 9 corresponds also to the position of B and E of FIGS. 5 and 6. Besides, the cam 39 which raises the assembly of segments is located at the point of its largest radius, its rotation sense being indicated by the arrow 47.

After a rotation at a determined angle of the segments, the cam 39 reaches the position of FIG. 11 (to which corresponds the opposite FIG. 12) in which it appears that the swinging plate 31 and all the organs it supports have been lowered angularly around the fixed shaft 32. This intermediate lowering is such that the nose 35 rests on the fixed stop 42. This is the position of FIG. 3, in which segments 13 and 20 and pressing organs 12 and 19 are lowered, but are still in contact, for the distance between the arbors 17 and 20 has not varied. It is still determined by the resting of the stop-screw 38 on a point of the swinging plate 31. It is also the position E of the curve of FIG. 6.

Later on, when the resting radius of the cam 39 on the small roller 40 has diminished further (13" of FIG. 6), the swinging plate 31 will have been lowered down to its lowest position in FIG. 13 (to which corresponds the opposite of FIG. 14) which corresponds to that represented in FIG. 4.

Since the nose 35, secured by the fixed stop 42, being unable to follow this movement, the yoke 34 will still be hung at that point, therefore swinging around the shaft 30, common to the cog-wheel 29.

There is separation between the stop-screw 38 and the swinging plate 31 and simultaneously parting from each other of the arbors 17 and 20. Thus, the condition of separation from each other of the segment and the pressing organ (FIG. 4) is fulfilled. The spring 36 is, of course, compressed accordingly.

These operations are repeated on each cycle, at least while the arrival of a gripping bar 4 (FIG. 2), the gripping, separation and lowering of a processed sheet (FIG. 3) and its insertion and passage into the ejecting device (FIG. 4) are taking place.

It has been noted that facing the wall 41 (FIG. 7) is a wall 43, while facing the swinging plate 31 a similar opposite plate and, facing the yoke 34 is a likewise opposite yoke. These organs serve in particular to support the ends of the arbors 17 and 20 opposite to those already described (FIGS. 11 and 13) and to impart to them motions identical with those already mentioned.

FIG. 10, opposite to FIG. 9 shows a swinging plate 48 opposite to 31 but with a somewhat different profile and the yoke 49 opposite to 34 and of same profile, with a nose 50 cooperating with the stop 51.

The plate 48 turns around the shaft 32 common to the plate 31, the yoke around the shaft 52 geometrically coaxial with the shaft 30, its position in relation to the plate 48 is fixed by the stop-screw 53 symmetrical to 38 and a rod 54 with drawback spring 55 which operates symmetrically with respect to the-rod 37 with spring 36.

If it is assumed that a cam 45 cooperating with a small roller 44 (FIG. 7), (both not represented in the FIGS. 10, 12 and 14 for simplicity) causes the plate 48 to oscillate identical with that governing the oscillations of the plate 31, and that the stop 51 operates identically as the stop 42 symmetrically opposed, it results therefrom that actually the two ends of the arbors 17 and 20 perform together the same motions, i.e. the cycle of motions already described.

These movements comply with all the working conditions as explained for FIGS. 1 to 6, with the exception of the variations of rotating speed of the segments and pressing organs corresponding to the curve C of the FIG. 5, i.e. acceleration from C until B and slowing down from B until C then back to the mean speed C.

The organs carrying out these changes are partly supported by the swinging plate 48 and visible, not only in FIGS. 10, 12 and 14, but also in part in FIG. 7 and mainly in FIG. 8.

With reference to these last two figures and to FIG. 10, a cam 56 governing this function is seen.

That cam, as well as the cams 39 and 45, turn with 6 the arbor 17 and at constant speed which the cog-wheel imparts to it, while the segments 18 turn Withthe socket 21 and according to a prescribed arrangement.

It has been seen how the cog-wheel 22 of socket 21 was driving the gears 29, 24, 25 and through the latter, the arbor 20 of the pressing organs, but it has not been mentioned how the socket itself was driven.

The socket 21 is driven from the cog-wheel 57, keyed on the arbor 17 and turning with the cams 39, 45, 56 and the driving cog-wheel 46, a group of two coaxial satellite wheels 58-59 transmitting the rotation to the cogwheel 23 of the socket 21.

The shaft of these satellite wheels is supported by a fork-lever 60 turning loosely around the arbor 17, which a system of connecting rods and levers can oscillate against the action of a return spring 61.

These elements have been represented in a diagrammatically simplified way, in FIGS. 10, 12 and 14, while in FIG. 8 the practical arrangement of them will be detailed further.

Beginning with the description of the simplified form of FIG. 10 the following arrangement is seen:

To the swinging plate 48 is joined a lever 62 pivoting around 63, supporting in its center a small roller 64, and the free end of which acts upon the connecting rod, linked to the lever 60, on the one hand and pushed by the spring 61 on the other hand. This thrust applies the small roller 64 against the cam 56.

Thus it is possible, through this cam, to impart to the lever 60 and to the satellite wheels it bears a swinging around the arbor 17.

The rotation sense of the latter and of the wheel 57 driving the satellite 58 are that of the arrow 66, and it is evident that, due to diameter differences of the wheels of these satellite wheels, a balancing toward the right of these during the rotation will cause a reduction of the multiplication ratio of the motions transmitted to the cog-wheel 23 and to the socket 21 (therefore to the segments 18 and to the arbor 20), Whereas an inverse balancing will cause an acceleration.

In FIG. 10 the cam 56 brings the small roller on its point of maximum radius, therefore as far as possible to the left.

In FIG. 12, corresponding to the positions of FIG. 11, the rotation of the cam has on the contrary caused a balancing of the lever 60 toward the right, during which a reduction of the rotating speed of the conveying organs took place.

In FIG. 14, corresponding to FIG. 13, the small roller 64 is on a concentrical circular zone of the cam 56. This is the immobility position of the satellite wheels, corresponding to an unvariable driving speed of the segments conveying the processed sheet.

In relation to the curves of FIGS. 5 and 6 and the preceding figures, these three cases correspond to the following positions:

FIG. 10 shows the assembly at a time beyond the period of acceleration of the sheet conveyance by the segments 18 and the pressing organs 19, in the slackening zone causing the separation of the sheet and of the conveying bar. The illustrated position is thus between B and C of the curve defining the speed of the said bar.

FIG. 12 corresponds to a position, as to conveying speed, during the acceleration coming after the point C before reaching the unvarying speed C.

The third and last position, represented in FIG. 14 corresponds to this latter case, in the circumstance the beginning of the curve portion C of FIG. 5 (unvarying mean speed of the segments and pressing organs 18 and 19).

Then the acceleration is renewed, and so forth, at the rate of one cycle by press working cycle, according to what has been described.

Thus and in addition to the displacements of the conveying organs 18 and 19 explained more particularly by 7 the FIGS. 9, 11 and 13, FIGS. 10, 12 and 14 show how to realize the accelerations and slackenings of the transport.

It has been stated that the cog-wheel 46 was the power wheel of the described assembly. On its turn it is driven by the cog-wheel 67, moved by the arbor 32, serving as an oscillating axle to all the described movable units. At last, it is thus this arbor, of immovable position, which allows to transmit the motive power to the whole mechanism and will establish the connection with the driving organs of the press.

The conveying bars, such as 4 of FIGS. 1 to 4, have been represented as driving the sheets to be processed in a plane coinciding with their upper face, on which are grips.

The described mechanism can of course also be applied when the sheet plane would coincide with the lower face of the bars, the parts being then located under instead of over the grips. However, in this case the segments 11 (FIGS. 1 to 4) respectively 18 (FIG. 7) should be arranged above the corresponding pressing organs.

What I claim is:

1. In combination, a punching press, a waste ejecting device and a delivery mechanism for transferring punched sheets from the press to the waste ejecting device, said press comprising a plurality of bars which engage successive sheets and transfer the sheets through the press for punching operations, means engaging the bars to periodically drive and immobilize thesame to alternately position the sheets between the press during a punching operation and thereafter drawing the thus punched sheets from the press, said bars reaching a maximum speed between successive immobilizations, means operative at constant speed for delivering punched sheets to the Waste ejecting device, said delivery mechanism comprising rotating means adjacent said press for engaging the sheets which are driven by said bars, means driving the rotating means at a variable speed in synchronism with the press and causing the rotating means to engage the sheets with a peripheral speed equal to that of the maximum speed of the bars and thereafter decelerate to remove the sheets from the bars, the rotating means being decelerated to a constant speed which is equal to the speed of the aforesaid means which is operative at constant speed such that the sheets can be transferred from the rotating means to said aforesaid means at said constant speed, said rotating means including profiled organs having a notched periphery to permit passage of the bars and thereafter engage the sheets which are conveyed by said bars and means engaging the rotating means to vary the position thereof with respect to the path of the bars to cause the sheets to be temporarily moved away from the bars when the latter are separated from the sheets and thereafter move the rotating means back to its orginal position for engaging subsequent sheets.

- 2. The combination as in claim 1, in which the profiled organs of the rotating means are arranged by pairs, one organ of which is over and the other beneath the path of passage of the sheets which it engages by seizing the sheets between them, one of said organs having a sector of increased diameter and a sector of reduced diameter to allow the bars to pass.

3. The combination as in claim 2, in which said sectors of said profiled organ defining a-notch, the organs being driven such that each bar passes through said notch only during an odd number of turns which is at least 3.

4. The combination as in claim 3, in which each organ has a rotary shaft, the shaft of one of said organs being secured by two parallel and movable platens which are raised and lowered periodically by cams, the shaft of the other of said organs being supported by yokes articulated to the said platens and taking rest against the stops of the latter such that the said yokes follow the platens in their up and down movement, but however are stopped during this displacement in one of the aforementioned directions, to cause a momentary separation of the said shafts and, with them, of the organs of said pair.

5. The combination as in claim 3, in which the means driving the rotating means comprises a satellite coupling comprising two wheels of dilferent diameter which a cam drives with a balancing motion around the shaft of one of the organs, said coupling being itself driven'by a rotatory member turning at constant speed, to accelerate and to slow down alternatively the organs.

6. The combination as in claim 5, comprising a rotatory power member driving the profiled organs onward around the shaft of which turn the two platens, While the raising and lowering cams of the platens run on small rollers coaxial of fixed shafts, the cam causing the balancing of the coupling of satellites being also coaxial to the one of said organs pivoted to the said platens.

References Cited by the Examiner UNITED STATES PATENTS 1,826,020 10/31 Post 27151 2,571,806 10/51 Wood 271-51 2,580,469 1/52 Schwartz 271-51 X 2,766,985 10/56 Claybourn 271-51 2,805,856 9/57 Stuckberg 27151 2,813,718 11/57 Plache 271--51 M. HENSON WOOD, JR., Primary Examiner.

ROBERT B. REEVES, Examiner. 

1. IN COMBINATION, A PUNCHING PRESS, A WASTE EJECTING DEVICE AND A DELIVERY MECHANISM FOR TRANSFERRING PUNCHED SHEETS FROM THE PRESS TO THE WASTE EJECTING DEVICE, SAID PRESS COMPRISING A PLURALITY OF BARS WHICH ENGAGE SUCCESSIVE SHEETS AND TRANSFER THE SHEETS THROUGH THE PRESS FOR PUNCHING OPERATIONS, MEANS ENGAGING THE BARS TO PERIODICALLY DRIVE AND IMMOBILIZE THE SAME TO ALTERNATELY POSITION THE SHEETS BETWEEN THE PRESS DURING A PUNCHING OPERATION AND THEREAFTER DRAWING THE THUS PUNCHED SHEETS FROM THE PRESS, SAID BARS REACHING A MAXIMUM SPEED BETWEEN SUCCESSIVE IMMOBILIZATION, MEANS OPERATIVE AT CONSTANT SPEED FOR DELIVERING PUNCHED SHEETS TO THE WASTE EJECTING DEVICE, SAID DELIVERY MECHANISM COMPRISING ROTATING MEANS ADJACENT SAID PRESS FOR ENGAGING THE SHEETS WHICH ARE DRIVEN BY SAID BARS, MEANS DRIVING THE ROTATING MEANS AT A VARIABLE SPEED IN SYNCHRONISM WITH THE PRESS AND CAUSING THE ROTATING MEANS TO ENGAGE THE SHEETS WITH A PERIPHERAL SPEED EQUAL TO THAT OF THE MAXIMUM SPEED OF THE BARS AND THEREAFTER DECELERATE TO REMOVE THE SHEETS FROM THE BARS, THE ROTATING MEANS BEING DECELERATED TO A CONSTANT SPEED WHICH IS EQUAL TO THE SPEED OF THE AFORESAID MEANS WHICH IS OPERATIVE AT CONSTANT SPEED SUCH THAT THE SHEETS CAN BE TRANSFERRED FROM THE ROTATING MEANS TO SAID AFORESAID MEANS AT SAID CONSTANT SPEED, SAID ROTATING MEANS INCLUDING PROFILED ORGANS HAVING A NOTCHED PERIPHERY TO PERMIT PASSAGE OF THE BARS AND THEREAFTER ENGAGE THE SHEETS WHICH ARE CONVEYED BY SAID BARS AND MEANS ENGAGING THE ROTATING MEANS TO VARY T HE POSITION THEREOF WITH RESPECT TO THE PATH OF THE BARS TO CAUSE THE SHEETS TO BE TEMPORARILY MOVED AWAY FROM THE BARS WHEN THE LATTER ARE SEPARATED FROM THE SHEETS AND THEREAFTER MOVE THE ROTATING MEANS BACK TO ITS ORGINAL POSITION FOR ENGAGING SUBSEQUENT SHEETS. 